Governor for motors



(No Model.)

2. Sheets-Sheet 1. J. DOW.

GOVERNOR FOR MOTORS.

Patented Jan. 12

[III/Ill I74/U67fl0 3 Joaiwz/jow IIIIIIA 'IIII II/IIII? (No Model.) 2SheetsSheet 2.

J. DOW.

GOVERNOR FOR MOTORS.

No. 334,112. Patented Jan. 12, 1886.

NITED STATES PATENT OFFICE.

JOSIAH DOlV, OF LOWELL, MASSACHUSETTS.

GOVERNOR FOR MOTORS.

SPECIFICATION forming part of Letters Patent No. 334,112, dated January12, 1886.

Application filed June 15, 1885. Serial No. 168,771. (No model.)

To all whom it may concern.-

Be it known that I, JOSIAH Dow, a citizen of the United States, residingat Lowell, in the county of Middlesex and State of Massachusetts, haveinvented new and useful Improvements in Governors for Motors, of whichthe following is a specification.

My invention relates to governors for steamengines, water-wheels, andsimilar motors; and the purpose thereof is to provide an apparatuswhereby an accurate differential adjustment shall be given to the valveor gate, through which the vapor or fluid passes to the motor, whereinthe adjusting devices. shall be driven by positive mechanism and theentire mechanical organization be greatly simplified and reduced inbulk.

The invention consists in the several novel features of construction andcombinations of parts hereinafter fully set forth, and definitelypointed out in the claims.

In the accompanying drawings, Figure 1 is avertical section in the plane1 1, Fig. 2, showing the casing with its interior mechanism, thecylinder-head being removed. v Fig. 2 is a central vertical section ofFig. 1, taken in the plane of the axis of the common shaft. Fig. 3 isaside elevation of the parts shown in Fig. 1, part of the cylindricalshell of the casing being removed. Fig. 4 is a side elevation of theclosed casing, showing the driving-shaft with its pulley and theadjusting-gear sleeved thereon at the opposite end of the shaft. Fig. 5is an end elevation of the closed casing, taken from the right of Fig.4.

In the said drawings, the reference-numeral 1 designates the casingwithin which the operative parts are assembled. This casing ispreferably made in cylindrical form, as shown, for the purpose of givingcompactness and reducing the bulk; but otherwise it forms no essentialfeature of my invention. An-angleplate, 2, is cast upon the lowerportion of the or shel14isdivided upon a central horizontal plane intotwo equal parts, as shown in Figs.

3 and 4; but the casing may be divided in any other suitable manner.Through the casing and coincident with its cylindrical axis is passed ashaft, 7, having its bearing in sleeves 8 and 9, mounted upon or neareach end of the shaft. These sleeves are supported in journal-boxes 10,cast integral with the cylinder-heads, and each has revolutionindependently of the movement of the shaft 7. Centrally mounted uponsaid shaft and rigid therewith is a hub, 11, and projecting radiallyfrom opposite sides thereof are two tubes, 12, tapped into said hub andcontaining in each a spiral spring, 13, attached at the end nearest theshaft to rigid pins 14.. Sleeved upon each of said tubes 12 is amiter-gear, 15, having a hub, 16, which is prolonged outwardly, as shownin Fig. 2. Surrounding these prolonged hubs or sleeves are cylindricalcaps 17, which rest upon the hubs of friction-gears 18, splined upon theprolonged hubs 16, and not i only having revolution therewith, but beingcapable of radial adjustment upon the same by the means presently to bedescribed. Upon the outer end of each tube 1.2 is turned a threadedtube-section,19, by which each mitergear 16 is held down upon a boss,20, formed upon the hub 11, each of said tube-sections 19 beingoutwardly flush with the prolonged hubs 16. Passing through the outerends of the cylindrical caps 17 are rods 21, connected to the outerextremities of the springs 13, and upon the exterior threaded ends ofthese rods are turned nuts 22, held by jam-nuts 23.- By thisconstruction it will be seen that while the frictiongears 18 must turnwith the miter-gears 15 they may at the same time, under a suffi cientcentrifugal force, be projected outwardly upon the prolonged hubs 16,upon which they are splined. \Vhen the centrifugal force producing thismovement is expended, the gears 18 will be returned to their originalposition by the tension of the spring 13. The cylindrical cap17 movesfreely outward and inward relatively to the shaft 7 but is preventedfrom turning by means of pins fixed upon the tubesections 19 andengaging with slots cut longitudinally in the inner faces of said cap.

Mounted or formed upon the inner end of the sleeve 9 is a double gearcomposed of a miter-gear, 24, of such diameter that it meshes with bothof the miter-gears 15 and a gear,

25, concentric with and lying in the same vertical plane with aninternal gear, 26, rigidly mounted upon the cylinder-head. The diameterof the internal gear is twice that of the gear 25, and between the two,upon opposite sides of the gear 25, are placed planet-gears 27, meshingwith both and having their axes arms 28, which are rigidly attached tothe hub 11. Upon the outer end extremity of the-sleeve 9 is mounted apulley, 29, by which rotation is imparted to the gear 25 and the mitergears 2%, said pulley being driven by a belt from any suitable part ofthe mechanism driven by said motor. Upon the sleeve 8 is splined a disk,30, having a diameter in excess of that of the friction-gear 18, saiddisk being held in frictional contact with the gears 18 by means ofsprings 31, interposed between a flange, 32, upon the sleeve 8, and thehub of the friction-disk 30.

By the construction and combination of parts heretofore described itwill be seen that the hub 11 will be caused to revolve about the shaft7, carrying with it the gearing mounted upon the tubes 12, and it isalso evident that the double gear 24 and 25 will accomplish tworevolutions while the hub 11 is making a single rotation. planet-gears27 being one-half the diameter of the gear 25, the latter will revolvethem twice to one of its own revolutions; but as said planet-gears alsomesh with the internal gear 26, which being twice the diameter of gear25 is therefore four times the diameter of said planetgear, the lattermust make four revolutions upon their own axes to pass once around theinternal gear. To cause these four revolutions, and to produce therefromone complete revolution of the hub 11, with its attendant gearing, thegear 25 must evidently make two revolutions. As the gears 24 and 25 maketwo revolutions about the common axis 7 to one made about the same axisby the gears 15, it follows that the gear 24 will cause gear 15 torevolve once upon its own axis in the same time-t. 6., it will revolveonce upon its own axis, while the bearing upon which it is mountedrevolves once about the common axis 7. Now, it is evident that if thefriction-gearsl8 have bearing upon the disk 30 at a distance from theaxis of the shaft 7 equal to the radius of the gears 18, the latter willmerely have rolling contact with said disk. In other words, let it beassumed that the frictiongears 18 have a radius of four inches, andconsequently a diameter of eight inches, their circumference willmeasure twenty-four inches If, now, said gears have contact with thedisk 30 at a point four inches from the axis of the shaft 7, and make asingle turn upon their own axes, while the bearing upon which said axesturn makes a' single revolution upon the common axis 7, the gears 18,which are driven, as already shown, by positive mechanism will simplyroll upon the disk 30, and the line in which they travel may bedenominated the neutral point of the disk. If, however,

This is due to the fact that the,

the speed becomes so great as to generate sufficient centrifugal forceto project the friction gears 18 outward upon their axes until theytravel in a circle beyond said neutral point, then said gears willimpart at each rotation a movement to the disk 30 proportioned to thedifference between the circumference of said disks and thelarger circleon which they travel, thereby carrying said disk in the direction inwhich they travel. For example, ifthe frictiongears make contact at apoint on the disk 30 distant radially five inches from the axis of thedisk, then at each revolution of the shaft 7 and of the gears 18 thedisk will receive a movement in the direction traveled by thefriction-gears of about six inches, measured upon the circle of contact,the equation being substantially (letting 0: represent the differencebetween the circumference of the gears and the line of travel) 103.14159:8 3.14159 x,- or, performing the operationsindicated, it will befound that the disk 30 will move with the gears a distance of 6.283inches measured upon the circle of contact. On the other hand, let it besupposed that the speed is so far decreased as to allow the tension ofthe spring to draw the gears 18 inward toward the shaft 7 to a point,say, three inches of radial distance from the axis of said shaft. Inthis case the relative speed of the gears beinga constant quantity, (aswell as their travel about the I common axis 7,) the disk 30 will berevolved in the opposite direction, its degree of movement being equalto the difference between the circumference of the actuatinggears andthe circle of contact. Letting 11 represent the relation of theperimeter to the diameter of each, the equation will then read, (lettinga: represent the difference as before) sXrr fiXvr-l-m; or, in otherwords, the disk 30 will receive a motion opposite to that of thefriction-gears equal to 6.223 inches for each revolution of said gears,said distance being measured upon the circle of frictional contact. Uponthe outer extremity of the sleeve 8 is mounted a miter or other gear,33, by which movement may be given to the device by which the steamportor water-gate is opened and closed.

Now, by applying to the described mechanism the explanation given above,it will be seen that if the speed of the motor increases either suddenlyor slowly the friction gears will be projected outwardly upon theirbearings against the inward draft of the springs 13 a distanceproportioned to the centrifugal force developed 'by such increase inspeed, thereby carrying the gears 18 beyond the neutral line upon thedisk 30,and causinga movement of the latter upon its own axis, whichwill gradually close the port and diminish the flow of steam. If, on theother hand, the speed falls below the average required, the tension ofthe springs 13 will draw the gears inward toward the common axis 7,giving frictional contact upon the disk 30 within the neutral circle,and producing at each revolution of the gears a movement of the disk,and consequently ICC IIO

of the gear 38, whereby the port will gradually be opened and anincrease of motive power supplied.

The device actuated by the disk 30 may be a train of gearing meshingwith the gear 33, or a simple rack-bar meshing with a spur-gear upon thesleeve 8.

I have indicated upon the disk 30 the neutral point of contact for thegears 18 by aline designated by the letter a. If the centrifugal forceis sufficient to project the gears beyond this point, the disk will movewith said gears, as already described; but if the speed is so fardiminished as to bring the gears within said point the disk will bedriven in the opposite direction.

By adjusting the tension of the springs 13, by means of the nuts 22 and23,the apparatus may be adapted to any load and to maintain a givenspeed under all circumstances.

WVhat I claim is- 1. In a governor for motors, the combination, withadisk having independent bearing, of a friction gear or gears bearingthereon, bearings radiating from the axis of the diskbearing upon whichsaid gears are adjustable longitudinally, said bearings being mountedupon an axis coincident with that of the disk, mechanism for impartingto said friction gearing and to the bearing upon which it is mountedsynchronous rotation, said mechanism being adapted to open and close asteam or other port by devices actuated by the revolution of said diskin opposite directions, substantially as described.

2. In a governor for motors, the combination, with a disk opening andclosing the port of the engine, of friction-gears bearing upon the flatface of said disk, radial bearings upon which said friction-gears arerotated and adjusted, a shaft carrying said bearings and havingsynchronous revolution with the frictiongears, and springs drawing saidgears toward the axis about which their bearings rotate, substantiallyas described.

3. In a governor for motors, the combination, with a shaft driven by anysuitable means, of a hub rigid thereon, tubes projecting radially fromopposite sides of said hub, miter-gears sleeved upon said tubes andhaving prolonged hubs held in place by nuts on the threaded ends of thetubes, friction-gears splined upon said prolonged hubs, springs drawingsaid gears toward the revolving shaft, a friction disk sleeved upon saidshalt with the plane face of which the friction-gears engage, and meansfor imparting to the shaft and to the said gears equal revolution inequal time, substantially as described.

4. In a governor for motors, the combination,with a diskjournaled uponanindependent axis, of friction-gears engaging with the plane face ofsaid disk, rotating bearings upon Which said gears are radiallyadjustable, and means for inipartirg to said bearing or to the gearsmounted thi reon equal and synchronous revolution in planessubstantially at right angles to each other, substantially as described.

5. In a governor for motors, the combination, with. a revolving shaftand hub rigid thereon, of tubular bearings radiating from said hub,miter-gears sleeved upon said bearings, friction-gears splined upon theprolonged hubs of said gears, a disk with a plane face of which thefriction-gears engage, a miter-gear meshing with the miters upon thetubular bearings, a spur-gear carried by the miter-gear, a stationaryinternal gear in the same plane with the spur gear, and planet-gearsmeshing with said spur and internal gear and rigidly connected with thehub upon the shaft, substantially as described.

6. In a governor for motors, the combination,with a friction-gearsplined upon the prolonged hub of an actuating-gear, of a bearing forthe latter mounted radially upon a rotating axis, a spring drawing saidfriction-gear toward the rotating axis, a disk with the plane face ofwhich the gear engages, and gearing whereby the friction-gear receives asingle rotation upon its bearing to each rotation of the axis carryingsaid bearing, substantially as described.

7. In a governor for motors, the combination,with a friction-gearsplined upon the prolonged hub of an actuating gear, of a bearing forthe latter mounted radially upon a rotating axis, a spring drawing saidfriction-gear toward the rotating axis, means for varying the tension ofsaid spring, a disk with the plane face of which the friction-gearengages, gearing whereby the latter receives a single rotation to eachrotation of the axis carrying its bearing, and devices actuated by thedisk for opening and closing the steam-port, substantially as described.

8. In a governor for motors, the combina tion, with a rotating support,oftubular bearings rigidly mounted thereon and containing spiralsprings, miter-gear revolvingupon said tubular bearings and havingprolonged hubs, friction-gears splined upon said hubs and drawn by thesprings toward the axis of the rotating support, a disk with a planeface of which the friction-gears engage upon sides of its axis, andgearing for giving equal rotation in equal times to the friction-gears,and the support carrying the tubular bearings, substantially asdescribed.

9. In a governor for motors, the combination, with a disk, with theplane face of which friction-gears engage upon opposite sides of itsaxis, of a spring coiled upon the sleeve of said disk and forcing itagainst the frictiongears, bearings upon which the latter revolve, arotating shaft carrying said bearings, and means for imparting to saidshaft and to the friction-gears equal rotation in equal times,substantially as described.

10. In a governor for motors, the combination,with astationary internalgear and aconcentric spur-gear, of planet-gears meshing with both, asleeve carrying said spur-gear and a miter gear and driven by suitablemeans, miter-gears meshing with the miter on the sleeve and mounted ontubular bearings carried by a hub,which is rotated by arms connectedwith the planet-gears, friction-gears splined upon the prolonged hubs ofthe initers, springs coiled Within the tubular bearings, and drawing thefriction gears toward the axis of the hub, devices for adjusting thetension of said springs, a disk with the plane face of which thefriction'gears engage, a sleeve on which the disk is mounted, a springbearing on the rear face of the disk, a common shaft carrying the sleeveof the disk, and of the actuating miter and spur gears, and gearingcarried by the former sleeve and actuating the devices opening andclosing the port of the engine, the parts being so proportioned that thefriction-gears revolve upon their axes in equal time with the revolutionof the hub carrying the tubular bearings, substantially as described.

In testimony whereof I affix my signature in presence of two Witnesses.

JOSIAH DOWV.

'Witncsses:

SAMUEL B. \VYMAN, GEo. H. STEVENS.

